Drop weight scale



March 16, 1937. E. J. VON PEIN ET AL DROP WEIGHT SCALE Filed Dec. 12,1935 3 Sheets-Sheet l NVENTOR W ATTORNEY March 16, 1937. VON E N ET AL2,074,005

DROP WEIGHT S CALE Filed Dec 12, 1935 3 Sheets-Sheet 2 PIC-1.2.

' ATTORNEY March 16, 1937. E. J. VON PEIN ET AL DROP WEIGHT SCALE FiledDec. 12, 1935 5 Sheets-Sheet 3 Patented Mar. 16, 1937 UNITED STATESPATENT OFFICE DROP WEIGHT SCALE poration of New York ApplicationDecember 12, 1935, Serial No. 54,002

15 Claims.

This case relates to weighing scales, particularly to capacity weightcounterbalancing \means for supplementing automatic counterbalancingmeans.

The object of the invention is to provide novel means for applying thecapacity weights singly.

More specifically, an object is to provide an impositive rotary drivefor causing application of a capacity weight.

Another object is to provide a manual release mechanism which upon eachoperation, no matter how prolonged, releases a rotary drive for onesingle revolution only, to cause application of a single capacityweight.

Still another object is to provide novel resetting or restoring meansfor the capacity weight applying means.

Other objects will appear from the further parts of the specificationand from the drawings, in

which:

Fig. 1 is a front view of the capacity or drop weight portion of thescale.

Fig. 2 is a section along lines 2-2 of Fig. 1.

Fig. 3 is a section along lines 3-3 of Fig.1.

Fig. 4 is a section along lines 44 oi Fig. 1.

Fig. 5 is a section along lines 5-5 of Fig. 3, and

Fig. 6 is a section along lines 6-6 of Fig. 5.

The capacity weight counterbalancing mechanism preferably supplements anautomatic counterbalancing mechanism which includes draft rod I0,through which the load is applied to intermediate beam H (see Fig. 1).The beam transmits the load force through a link l2 to an automatic loadcounterbalanclng and indicating system (not shown).

The scale frame i4 carries the usual dial l5 having indications forcoacting with the pointer (not shown) to indicate the automaticallycounterbalanccd load.

When the automatic capacity of the scale is exceeded, one or more offour drop weights I6 is applied to the intermediate beam H to oppose theload.

The drop weights are each designed to counterbalance a load of 1000 lbs.As indicated in Figs. 1 and 2, each of the drop weights is formed at thebottom with a narrow rib l'l adapted to engage the baseof a taperednotch l8 formed in a horizontal strap I. which is fastened at oppositesides to the sides of a cage 20. The cage 20 is supported, at its upperend, by a knife edge 22 fixed in the right end of beam I I, and at itslower end the cage is pivoted to a check link 23 which combines withlever II to restrict cage 20 to ver- 55 tical movement parallel toitself.

In addition to supporting drop weights l6 by strap 19, cage 20 also hasa cross rod 24 on which hooks 25 of the integral stems 25 of weights I6rest when the drop weights are lowered. Rod 24 is formed between stems26 of the drop weights with enlarged knob portions 2'l which guide thedrop weights for vertical, rectilinear movement. When a drop weight islowered, it is supported by strap l9 and rod 24 of cage 20 and, throughthe cage, the weight is applied to beam H to oppose the force of theload.

The upper end of each weight stem is formed as a hook 28 to engage overa pin 29 carried by the lower end of a link 30 which has an elon-'gated, vertical, slot 3! receiving a rod 32 secured to frame standard33. Each link 30 is suspended from the right end of one of four bellcranks 34 and is constrained by rod 32 to substantially verticalrectilinear movement.

Each bell crank 34 is connected by a link 35 2 (see Figs. 3 and 5)'to anarm 36 pivotally suspended from a rod 31 fixed between the front andrear plates 38 and 38, respectively, of a subframe attached to mainscale frame l4.

Each pivoted arm 36 carries a roller 39 (see Figs. 3 and 6) for engagingthe periphery of a. difierent cam 40. The four earns 40 are pinned to acommon shaft 42 journaled in the front and back plates 38 and 38'. Ininitial, zero capacity weight position, each cam 40 has its low portionopposite the follower roller 39 of the associated link 36. A spring 43(see Fig. 2) acting on each bell crank 34 urges the bell crankcounterclockwise (Fig. l) to force link 35 to the left and to hold link30 and the drop weight l6, carried thereby, raised. As link 35 is urgedto the left, it causes follower roller 39 of the connected link 36 tomaintain engagement with the associated cam 40. When all the cams 40have their low portions opposite follower rollers 39, the drop weightsl6 are thus held in elevated position by the force of springs 43. Noneof the drop weights are then acting on beam l I and the capacity weightcounterbalancing effect is zero.

The spring 43 acting through each bell crank 34 exerts just enough forceto overcome by a bare minimum the gravitational force of the associateddrop weight. Therefore, a follower roller 39 presses only lightlyagainst the periphery of its cam 40 when the associated drop weight isin elevated position and opposing the pressure of spring 43 so that theresistance of the follower roller 39 to rotation of its cam 40 isreduced to a minimum and consequently the force required to 5 Cams 40are intended to act successively on the drop weights I6. Accordingly,the rise of each cam is offset from the rise of the next cam by an angleof 72 or one-fifth of a full turn of shaft 42. During the first fifth ofa revolution of shaft 42 clockwise (Fig. 5), the rise of one cam willact on a follower roller 39 to rock pivoted arm 36 counterclockwise,which through link 35 rocks the connected bell crank 34 clockwise. Asthe bell crank rocks clockwise, it lowers the connected vertical link 30and the weight l6 supported by pin 29 of the link. The Weight l6, as itdescends, engages strap [9 and rod 24 of cage 20 and stops moving downrelative to the cage while link 30 continues its descent and its pin 29releases hook 28 of weight stem 26. Thus, the first fifth of arevolution of shaft 42 applies one drop weight l6 to the beam tocounterbalance 1000 lbs. of load.

During the second fifth of a revolution, the rise of another cam willact on coacting follower roller 39 to cause another drop weight [6 to beapplied to beam H. i

In above manner, the first, second, third, and fourth fifths of a turnof shaft 42 will successively apply the four drop weights E6 to beam Hto counterbalance 1000 to 4000 lbs.

To indicate the capacity counterbalancing force in effect, theindicating dial l5 (see Fig. 1) has a sight opening 45 behind which isan indicating fiag 46 with successive 1000, 2000, 3000 and 4000indications. Initially, an unmarked portion of fiag 46 is at sightopening 45. As successive drop weights I6 are applied, flag 46 will risetosuccessively expose through opening 45 the indications 1000, 2000,etc.

To operate flag 45, shaft 42 rigidly carries a cam 41 (see Figs. 3, 5,and 6) engaged by a follower roller 48 carried by an arm 49 pivotallysuspended from rod 31. The lower end of arm 49 is connected by a link 50to a pivoted arm 5! rigidly carrying capacity indicator flag 46 (seeFig. 1). A spring 52 urges arm 5| counterclockwise (Fig. 1) to hold flag46 in lower position with its blank portion exposed through sightopening 45. As arm 5| is urged counterclockwise, it acts through link 50to hold follower roller 48 of arm 49 against the periphery of cam 41.

Cam 41 has a contour progressively increasing in radius in accordancewith the successive rises of earns 40. In the initial, zero capacityposition of the parts, the low portion of cam 41 is engaged withfollower 46. As shaft 42 is turned to cause cams 40 to successivelyapply the four weights l6 to beam i l, the cam 41 progressively movesfollower roller 48 and its arm 49 towards the right. As arm 49 moves tothe right, through link 56, it rocks arm 5i and flag 46 clockwise. Therise of cam 49 is so proportioned that upon the first, second, third,and fourth fifths of a turn of shaft 42, flag 46 will be raised tosuccessively expose 1000, 2000, 3000, and 4000 through sight opening 45.Since these successive increments of movement of shaft 42 also apply thefour weights E6, in succession, to beam II, it is evident that flag 46will indicate the counterbalancing effect of the applied weights.

After the rise of a cam 46 has acted on a follower 39, a high dwellportion of the cam engages the follower for the remainder of thefour-fifths of a revolution which shaft 42 is permitted to make; so thatonce a weight l6 has been applied to beam H, it remains in effect forthe rest of the partial revolution of shaft 42.

Shaft 42. rigidly carries a gear 52. When shaft 42 has rotatedfour-fifths of a turn clockwise, a stud 53 on the gear strikes a stoppin 54 (see Figs. 5 and 6) extending from back plate 38 and stopsfurther clockwise rotation of the shaft.

Gear 52 meshes with a gear 55 which is meshed with a pinion 56 on ashaft 51 (see Figs. 4, 5, and 6). Shaft 51 is urged clockwise by a drumspring motor 58. Normally, shaft 51 is restrained from clockwiserotation by engagement of the nose end of a pawl 59 with the base of anotch 60 in a one-revolution clutch disk 62 fixed to shaft 51. A spring63 biases pawl 59 anticlockwise to main: tain its nose end engaged withclutch disk 62.

Pawl- 59 has a horizontally extending arm 59b engaged at the bottom byarm 64a of a by-pass dog 64. The dog'is pivotally carried by thehorizontally disposed arm of a bell crank lever 65 and urged by a spring66 to engage its tall with a stop pin 61 on the, lever. The lower end oflever 65 is formed with a tab portion 68 extending through a hole infront plate 38 and exposed through a similar hole in scale frame l4 tobe 60 of clutch disk 62, permitting spring motor 58 to rotate shaft 51clockwise.

While arm 65 rocks clockwise to effect release of pawl 59 frqfn disk 62,the resisting pressure of pawl 59 exerted on arm 64a of dog 64 and theforce of spring 66 combine to maintain the tail of the dog firmlyagainst stop pin 61 of lever 65, thereby compelling the dog-to move as arigid part of lever 65.

As soon as dog 64 releases pawl 59 from disk 62, spring motor 58startsrotating shaft 51 and its disk 62 clockwise. The dog holds pawl 59released long enough to permit the notch 60 to pass the nose end of thepawl. Then, as lever 65 and the dog 64 continue to rock clockwise, thedog slides off to the right of arm 59b ofthe pawl, which is thereuponrestored counterclockwise by its spring 63. By this time, the unbrokencircular portion of disk 62 is opposite the nose end of thepawl so thatfor the remainder of the one revolution of disk 62, the pawl will rideon the circular portion of the disk. Near the end of the one revolutionof disk 62, its notch 60 will again reach the nose end of pawl 59 andthe latter will immediately be forced by spring 63 into the notch toengage the base of the notch to stop disk 62 when shaft 51 has completedits one. revolution.

When the operator releases pressure on-tab 68 of lever 65, spring 69restores the lever counter-' clockwise. Pawl arm 59b beingat this timebelow arm 64a of dog 64, the latter arm will strike arm 59b duringcounterclockwise movement of lever 65. Since pawl 59 is now engaged withthe circular periphery of disk 62, it cannot rock further.counterclockwise and arm 59b cannot move down. Therefore duringcounterclockwise movement of lever 65, when arm 64d strikes the top ofarm 59b, dog 64 is compelled by engagement with arm 59b to rockclockwise about its pivot, spring 66 yielding to permit this action ofdog 64. The dog yields relative to lever 65 until it passes-arm 59b ofpawl 59, whereupon spring 66 snaps the dog back into contact with stoppin 61. Thus, dog 64 provides a momentary operating connection betweenlever 65 and pawl 59 during the forward, clockwise stroke of the leverand yields relative to the'lever upon the return stroke of the lever inorder to pass by the pawl and return to its initial position beneath arm64b of the pawl.

Each time lever 65 is rocked by the operator, it effects release of disk62 and its shaft 51 for one revolution clockwise by spring motor 58.Through gearing 56, 55, and 52, one revolution of shaft 51 effectsone-fifth of a revolution of shaft 42 clockwise. As explainedpreviously, each fifth of a revolution of shaft 42 applies one ofweights l6 to beam The operator must depress lever 65 four times tocause application of the four weights I6 to beam A fifth depression oflever 65 will have noeffect since after four revolutions of shaft 51 andthe corresponding four-fifths of a revolution of shaft 42, pin 53 willbe against stop pin 54.

In order to dampen the speed of rotation of shaft 51 and the partsdriven thereby, a governor 18 is driven through gears 1|; 12, and 13from shaft 51.

After a weighing operation during which one or' more of the four weights|6 has been applied to counteract part of the load, the applied weightor weights must be returned to inactive position. This is done byrotating shaft 42 counterclockwise. During the counterclockwise rotationof shaft 42, through gears 52, 55, and 56, shaft 51 is also rotatedcounterclockwise to rewind spring motor 58.

To rotate shaft 42 counterclockwise, the following means are provided:

Shaft 42 has a gear 15 meshed with a gear 16 fast to a sleeve 11rotatably carried by a shaft 18 (see Figs. 3, 5, and 6). Sleeve 1]rigidly carries a driven clutch disk 19 having a single notch 88 forreceiving the nose of a clutch dog 8| urged towards the disk 19 by aspring 82. Dog 8| is pivotally carried by a driving disk 83 fast toshaft 18. The end of shaft 18 adjacent front plate 38 carries a crankhandle 84. Through this handle, the operator rotates shaft 18 clockwise.During clockwise rotation of shaft 18, clutch dog 82 carried by disk 83,fast to the shaft, engages the base of notch 88 of clutch disk 19 torotate the latter, its sleeve 11, and gear 16 on the sleeve clockwise.Gear 16, in turn, rotates gear 15 and cam shaft 42 counterclockwise toeffect restoration of the drop weights; shaft 42 through gears 52, 55,and 56 simultaneously rotates shaft 51 to restore the power of springmotor 58.

Gears 15 and 16 are in one-to-one ratio. Accordingly, during applicationof drop weights l6 upon each fifth of a revolution clockwise of shaft42, gear 18 will be rotated one-fifth of a revolution counterclockwise.Thus, starting from the initial position indicated in Fig. 5, gear 16,its sleeve 11, and driven clutch disk 19 will be rotatedcounterclockwise one to four fifths of a revolution depending on thenumber of drop weights applied to beam After the maximumcounterclockwise movement of four-fifths of a revolution, disk 19 willhave its notch 88 slightly less than one-fifth of a turn below the noseend of restoring dog 8| when the latter is in the initial position,shown in Fig. 5. Thus, when shaft 118 is subsequently rotated clockwise,pawl 8| will move down substantially one-fifth of a revolution before itseats in notch 88 and couples disk19 to shaft 18 for clockwise rotation.One revolution of shaft 18 in a clockwise direction will rotate sleeve11 a maximum of four-fifths of a revolution (plus a slight overthrow)during which all the four drop weights l6 are restored. by springs 43,under control of cams 48.

During the clockwise revolution of shaft 18, it is restoringspring-driven shaft 51 in a counterclockwise direction. At the end of asingle revolution of shaft 18, it will have caused a maximum of fourcounterclockwise turns of shaft 51 plus a slight overthrow movement.Thus notch 68 of clutch disk 52 on shaft 51 will have passed slightlybeyond the lower end of arm 59a of pawl 59. At this time, the tail ofclutch dog 8| of restoring disk 83 will strike a fixed stud 85 andthereby be rocked out of engagement with notch 88 of driven disk 19.

As a result, disk 19 is released for counterclockwise operation, andsince notch 68 of disk 62 has passed slightly beyond pawl 59, springmotor 58 is permitted to rotate shaft 51 clockwise a slight amountbefore the base of notch 68 engages the pawl arm 59a. During this slightclockwise rotation of shaft 51, it effects a corre spondingly slightcounterclockwise movement of disk 19, causing the base of notch 88 ofdisk 19 to move above the nose of clutch dog 8|. As a result, after onerestoring revolution of shaft 18, its clutch dog 8| is automaticallyreleased from driven disk 19 and engaged with the unbroken circularperiphery of disk 19, so that continued rotation of shaft 18 in aclockwise direction will not affect disk 69, cam shaft 48, or springoperated shaft 51.

Summary Assume a load of 2300 lbs. to be applied to the scale and thatthe automatic capacity of the scale is 1000 lbs. Application of the loadmoves the load pointer (not shown) beyond the limit of indicatingcapacity of dial !5. The operator thereupon presses on finger tab 68 oflever 65 to rock the latter clockwise. Dog 64 carried by lever 65 risesand acts on the arm 59b of pawl 59 to rock the latter clockwise,releasing its nose end from notch 68 of clutch disk '82. As dog 64rises, it passes arm 59b of the pawl which thereupon returns under theinfluence of spring 63 towards disk 62. The latter meanwhile has beenmoved clockwise by spring motor 58 so that notch 68 is above the noseend of pawl 59; the disk therefore continues its rotation to complete asingle revolution before being stopped by engagement of the base ofnotch 68 with the nose end of pawl 59.

The clockwise revolution of disk 62 and its shaft 51, through gears 56,55, and 52 drives shaft 42 for a fifth of a revolution, also clockwise,during which one cam 48 acts on a follower 39 to rock a pivoted arm 36counterclockwise. As the arm 36 moves counterclockwise, through a link35, it rocks a bell crank 34 clockwise, causing the latter to lower aweight supporting link 38. Descent of the latter drops a weight |6 ontosupporting strap I9 and rod 24 of a cage 28 hung from beam The weight l6when applied to beam offsets 1000 lbs. of the load. 1300 lbs. of theload still is acting on the automatic counterbalancing means, the latteris still beyond its indicating capacity, and therefore the operatordepresses lever 65 again to cause another revolu tion of shaft 51 and acorresponding fifth of a revolution of shaft 42 to take place. Duringthe second fifth of a turn of shaft 42 another cam 48 operates to effectapplication of a second drop weight [6 to the beam The capacitycounterbalance means will now be offsetting 2008 lbs.

will drive disk l9, its sleeve shaft i1 and gear 76 on the latter shaft,clockwise.

Gear it meshes with gear on shaft 52 and drives the lattercounterclockwise for two-fifths of a revolution, thus resetting thelatter and its cams til in their initial position. During the resettingof cams-i0, the two applied weights I6 are released from effect on beamH. As shaft 42 is returned, through gears 52, 55, and 56, it rotatesshaft 51 for two revolutions to re-energize spring motor 58.

It is to be understood that variations, changes, and modifications ofthe illustrated form of the invention may be made without departing fromthe teachings of the invention. It is therefore intended to be limitedonly in accordance with the scope of the appended claims.

What is claimed is as follows:

1. In a scale; a load responsive member, a plurality of weights, each tobe applied to said member to oifset a-predetermined load, a weightapplying mechanism, a device operable in steps, and upon each stepcausing said mechanism to apply one weight to said member, reciprocatingmeans for initiating operation of said device, and means separate fromand acting independently of the reciprocating means for restrictingoperation of said device to a single step upon each reciprocation of theinitiating means.

2. In a scale; a load responsive member, a plurality of weights, each tobe applied to said member to offset a predetermined load, a weightapplying mechanism, a device operable in steps, and upon each stepcausing said mechanism to apply a single weight to said member, meansmovable from and back to a starting point for initiating operation ofsaid device, and means separate from and acting independently of theinitiating means, upon said device for restricting operation of saiddevice to a single step upon each movement of the initiating means fromand back to its starting point.

3. In a scale, a load responsive member, a plurality of weights, each tobe applied to said member to offset a predetermined load, a weight ap-.

plying mechanism, a device operable in steps, and upon each step causingsaid mechanism to apply a single weight to said member, restrainingmeans for restraining operation of said device in a direction to applyweights, an instrumentality movable to a position for releasing therestraining means from eifect on the device so as toinitiate operationof said device, and means separate from and acting, independently of theaforesaid instrumentality, to restore said restraining means to effectupon said device for restricting operation of the device to a singlestep upon each movement of the aforesaid instrumentality to saidposition and regardless of the maintenance of said instrumentality insaid position.

a. In a scale; a load responsive lever, a plurality of weights, each forapplication to the lever to offset a predetermined load, aweight-applying mechanism, a rotatable drive, means coacting with thedrive and said mechanism for causing the latter to apply a singleweightupon each revolution of said drive, a manual member having alimited movement for initiating rotation of the drive, and meansrestricting rotation of the drive to a single revolution upon each saidmovement of the member.

5. In a scale; a load responsive lever, a plurality of weights, each forapplication to the lever to offset a predetermined load, aweightapplying mechanism, an impositively driven shaft, a clutch diskcarried by the shaft, a pawl coacting with the' clutch disk to restrainrotation of the shaft, and a manually operable element movable in onedirection to first engage and then pass by the pawl and by such actionmomentarily releasing the pawlfrom the disk to permit said shaft to berotated to a limited extent such as to cause said mechanism to applyonly a single weight to the lever.

6. In a scale; a load responsive lever, a plurality of capacity weights,each to be applied to said lever to offset a predetermined load, ashaft, mechanism operated by the shaft upon each revolution thereof forapplying one weight to the lever, a spring motor for rotating the shaft,a one-revolution clutch disk carried by the shaft, apawl for coactingwith the disk to prevent rotation of the shaft by the spring motor, andmeans for momentarily releasing the pawl from the clutch disk to releasethe shaft for a single revolution by the spring motor, during whichrevolution said shaft operates the weight applying mechanism to apply asingle weight to said lever.

'7. In a scale; a load responsive lever, a pinrality of capacityweights, each to be applied to said lever to offset a predeterminedload, a shaft, a weight-applying mechanism operated by a singlerevolution of the shaft to apply one weight to the lever, a spring motorfor rotating the shaft, 2. one-revolution disk on the shaft, a pawlcoacting with the disk to restrain rotation of said shaft, areciprocatable member, and means on said member for releasing the pawlfrom the disk to permit the shaft to make only one revolution upon eachreciprocation of said member.

8. In a scale; a load responsive lever, a plurality of capacity weights,each for application to said lever to offset a predetermined load, acyclically operable shaft, a weight-applying mechanism operated by theshaft to apply one weight upon each cycle of the shaft, and impositivedrive for the shaft, a clutch disk on the shaft, a pawl coacting withthe disk to restrain rotation of the shaft, a manually reciprocatablemember, and a by-pass dog on the member coacting with the pawl upon eachreciprocation of said member to momentarily release the pawl from thedisk to permit one cycle of operation of the shaft for causing the saidmechanism to apply one weight to the lever.

9. In a scale, a load responsive member, a plurality of capacity weightsapplied to the member to offset predetermined loads, means for removingthe weights from effect on the member, a rotary actuator effective upona single revolution to operate said means to remove the weights fromeflect on said member, and one-revolution clutch means for driving saidactuator through one revolution and then automatically releasing saidactuator.

10. In a scale, a load responsive member, a plurality of capacityweights applied to said member to ofiset predetermined loads, means forremoving the weights from effect on the member, an actuator having acycle of operation during which it operates said means to remove saidweights from efiect on the member, manual means for operating saidactuator, and means for antomatically releasing the manual means fromthe actuator when the latter has been operated through its cycle ofoperation.

11. In a scale, a load responsive member, a plurality of weights appliedto said member to 011- set predetermined loads, means for removing theweights from effect on the member, a driven clutch device for operatingsaid means, a driving clutch device coacting with the driven clutchdevice for operating the latter, and means other than and actingindependently of the load re= sponsive member for automatically stoppingop eration of the driven clutch device by the driving clutch device whenthe driven clutch device has been moved through a predetermined stroke.

12. In a scale, a load responsive member, a plurality of weights,mechanism movable in one direction to successively apply the weights tosaid member to offset predetermined loads and mov aiole in a reversedirection to cause the weights to be removed from said member, a drivende vice connected to said mechanism to move in synchronism therewith, adriving device having a certain cycle of operation, coupling meansbetween the two devices for picking up the driven device at differentpoints or" said cycle oi opera= tlon depending on the number of weightswhich have been applied and thereafter actuating the driven device tomove said mechanism in said reverse direction, and means forautomatically rendering the coupling means inefiective when the appliedweights have all been removed from the member.

13. In a scale, a load responsive lever, a plurality of capacity weightsto be applied to said lever to oflset predetermined loads, mechanism forapplying the weights to and removing them from the lever includingelements movable in one direction to cause application of the weights tothe lever and movable in the reverse direction to cause the weights tobe removed from said lever, a common shaft for said elements, a drivenclutch device connected to-saicl shaft, a driving clutch device, meansfor coupling the driving device to the driven device to move the latterand said shaft in a reverse direction to cause the elements to removesaid weights from the lever, and means for rendering the coupling meansineifective to transmit operation of the driving de= vice to the drivendevice upon continued operation of the driving device after the drivende= vice has been restored to a predetermined poshtion.

14-. In a scale, a load responsive member, a plurality of weights to heapplied to'said meinloer to chest predetermined loads, mechanism iorapplying the weights to and removing them from said member, a springactuator for operating smd mechanism to apply the weights to saidmember, and a restoring actuator for operating said mesh-=- anism toremove the weights from the member and to simultaneously store up energyin the spring actuator.

15. In a scale, a load responsive meinher, a Weight to he applied tosaid member to cheat a predetermined load, a earn, linkage including acam follower for applying the weight to the mem loer upon operation ofsaid cam, and spring means connected to the linkage and acting thereonin opposition to the gravitational iorce oi the weight to maintain thefollower lightly pressed against the cam.

EWARD J. VON PEIN. PAUL J. SCHLEZESIGER.

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